CN102996471A - Turbine compressor - Google Patents
Turbine compressor Download PDFInfo
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- CN102996471A CN102996471A CN2012103358442A CN201210335844A CN102996471A CN 102996471 A CN102996471 A CN 102996471A CN 2012103358442 A CN2012103358442 A CN 2012103358442A CN 201210335844 A CN201210335844 A CN 201210335844A CN 102996471 A CN102996471 A CN 102996471A
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- stage compressor
- lubricating oil
- oil tank
- compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
- F04D17/12—Multi-stage pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/028—Units comprising pumps and their driving means the driving means being a planetary gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/002—Details, component parts, or accessories especially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/403—Casings; Connections of working fluid especially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
- F16H1/06—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2210/00—Working fluids
- F05D2210/10—Kind or type
- F05D2210/12—Kind or type gaseous, i.e. compressible
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/60—Fluid transfer
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention relates to a turbine compressor, wherein a gearbox is provided with an input shaft and at least one pinion shaft used for receiving the rotation of the input shaft transmitted through a gear. A first-stage compressor and a second-stage compressor are driven by the above pinion shaft. Gas coolers used for cooling gases output by the first-stage compressor and the second-stage compressor are respectively provided. The lower part of the gearbox is provided with a lubricating oil tank. The two side surfaces of the lubricating oil tank, which are positioned close to the first-stage compressor and the second-stage compressor, are provided with the gas coolers respectively. The axes of the gas coolers, the axis of the lubricating oil tank and the input shaft are arranged in parallel with each other. In this way, the space for the compressors is not increased or decreased by the mechanical loss due to the rebounding of the lubricating oil. Meanwhile, the pipe construction for cooling water is enabled to be easier.
Description
Technical field
The present invention relates to from the multistage turbocompressor of live axle via the gear internally-arranged type of the running shaft of driving gear drives impeller.
Background technique
At first, for the multistage turbocompressor of relevant past case, 6～Fig. 9 describes referring to accompanying drawing.Fig. 6 is the plan view of the centrifugal compressor of relevant conventional art 1, Fig. 7 is that IV-IV of Fig. 6 is to view, Fig. 8 is the sectional view of the turbocompressor of relevant conventional art 2, and Fig. 9 is the example that the turbocompressor with relevant conventional art 2 arranges the cooling water pipe system diagram in many situation.
The structure that has the compressor base portion 45, gearhousing body 46, first order scroll portion 47, second level scroll portion 48 and the motor mounting platform 49 that possess respectively hollow structure, these each ones are formed by casting about the compressor main body 44 of the centrifugal compressor of conventional art 1.
And, the inside of compressor base portion 45 by on the part of an end A side, be formed with the lubricant oil that accumulates lubricant oil and accumulate chamber 52, the inside of compressor base portion 45 by on the part of the other end B side, be formed with the interstage cooler chamber 50 of in-built heat exchange elements (not shown) and the aftercooler chamber 51 of in-built other heat exchange elements (not shown).
In addition, leaning on the end of an end A side of compressor base portion 45, opening portion lid 59,60 is installed, so that it divides respectively open covering with the opening portion 56,57 that lubricant oil accumulates chamber 52, leaning on the end of the other end B side of compressor base portion 45, opening portion lid 58 is installed, so that its opening portion 54,55 with interstage cooler chamber 50, aftercooler chamber 51 covers integratedly.
In above-mentioned opening portion lid 58, be provided with internally to be contained in the pipeline (not shown) that the heat exchange elements in the two cooler chambers 50,51 carries out the handing-over of cooling medium, by cooling medium is circulated to each heat exchange elements from the outside of compressor base portion 45, between the gas of this cooling medium and two cooler chambers 50,51 inside, carry out heat exchange, above-mentioned gas is cooled off.In addition, be provided with gas outlet (not shown) to outside opening in above-mentioned aftercooler chamber 51.
And then, inside in first order scroll portion 47, near the first order by extending the end A side end that is formed with the interstage cooler chamber 50 of the inside from vortex chamber 62 to above-mentioned compressor base portion 45 stream 66 that spues, by impeller (not shown) rotation, flow into from gas access 65 first order scroll portion 47 and compressed gas flow in the interstage cooler chamber 50 through the first order stream 66 that spues.
And then, inside in second level scroll portion 48, be formed with near the second level suction passage 70 by extending to vortex chamber 67 the other end B side end of the interstage cooler chamber 50 of the inside of above-mentioned compressor base portion 45, near and the second level by extending the other end B side end of the aftercooler chamber 51 from vortex chamber 67 to the compressor base portion 45 inside stream 71 that spues, by vane rotary, flow into the second level scroll portion 48 and compressed gas flow into (for example with reference to Japanese kokai publication hei 7-103162 number) in the aftercooler chamber 51 through the second level stream 71 that spues from second level suction passage 70.
But, the part of the pipe arrangement (not shown) that is connected with above-mentioned cooler chamber 50,51 about the centrifugal compressor compressor main body 44 of the conventional art 1 and interstage cooler chamber 50 and aftercooler chamber 51 and with compressor main body 44 is integrated structure, owing to be formed with base plate 61a in the bottom of the gearhousing body 61 of taking in overdrive gear, meet above-mentioned base plate 61a and rebound so be injected into lubricant oil in this gearhousing body 61, collide on the overdrive gear and mechanical loss is increased.As a result, the hydraulic performance decline that causes centrifugal compressor.
On the other hand, although conventional art 2 will be by the gear-box 81 of taking in overdrive gear (not shown), the compressor main body that the 1st stage compressor 85 and the 2nd stage compressor 86 consist of, the 1st gas cooling section 82 and the 2nd gas cooling section 83, and the part of the pipe arrangement that the above-mentioned compressor main body is connected with the 1st gas cooling section 82 and the 2nd gas cooling section 83 (for example, 1 grade of pressurized air circulation flow path 88 or 2 grades of pressurized air circulation flow paths 89) to have made the Construction integration this point identical with above-mentioned conventional art 1, but as shown in Figure 8, directly lubricant oil is recovered to structure (with reference to No. the 4048078th, Japan's special permission) in the lubricating oil tank 87 for the base plate of having removed gear-box 81.Thereby, do not have as conventional art 1, lubricant oil meets above-mentioned base plate 61a and rebound, make mechanical loss to increase, cause the situation of the hydraulic performance decline of centrifugal compressor.
But, the turbocompressor of relevant conventional art 2 like this is same with the centrifugal compressor of relevant conventional art 1, in conventional art 1, be interstage cooler chamber 50 and aftercooler chamber 51 at the 1st gas cooling section 82 and the 2nd 83(of gas cooling section) axial direction (length direction of the 1st gas cooling section 82 and the 2nd gas cooling section 83) along with the direction configuration of live axle (not shown) quadrature of pinion shaft 84 configurations that are parallel to compressor.In addition, the drive motor that drives above-mentioned live axle certainly along and the live axle coaxial direction install, so the boundary dimension of such compressor is long on the direction parallel with live axle, with the direction of this live axle quadrature on shorter.In addition, mouth is coordinated in the water supply of the cooling water of the 1st gas cooling section 82 and the 2nd gas cooling section 83 and draining is coordinated on mouthful end of the axial direction that is configured in these the 1st gas cooling sections 82 and the 2nd gas cooling section 83.
Arrange in the turbocompressor with relevant conventional art 2 in many situation, for the convenience of safeguarding, as shown in Figure 9, should many turbocompressor be configured to, make the live axle of each compressor arranged side by side.As a result, to each cooling part 82,83 water supply coordinate mouthfuls 91 and draining coordinate mouthfuls 92 and be configured on the side (the mutual opposed face in the face of adjacent compressor) of each compressor.
In the situation of like this configuration, coordinating mouth 91 and the draining coordination mouthful 92 water supply piping 91a that connect and drainage piping 92a to supplying water all need to be with respect to supplying water main pipe arrangement 91b and draining master pipe arrangement 92b bending (namely, roughly crooked to right angle orientation, be connected on each compressor so that supply water the extension of main pipe arrangement 91b and draining master pipe arrangement 92b almost parallel ground with this after generally perpendicularly extending from supply water main pipe arrangement 91b and draining master pipe arrangement 92b) and pipe arrangement, pipe arrangement construct complicated and difficulty.In addition, need to guarantee sufficient space for the operation of extracting of the maintenance of each drive system and cooler body at each compressor chamber, so need the larger space that arranges.
Summary of the invention
Thereby, the purpose of this invention is to provide a kind of mechanical loss of bringing because of rebounding of lubricant oil of not making and increase, make arranging that the space diminishes and can making the pipe arrangement construction of the cooling water easy turbocompressor that also becomes of compressor.
In order to achieve the above object, relevant turbocompressor of the present invention, have on input shaft and the acceptance side via the gear-box of at least 1 pinion shaft of the rotation of the next above-mentioned input shaft of gear transmission, possess by shaft-driven the 1st stage compressor of above-mentioned small gear, and possess by shaft-driven the 2nd stage compressor of above-mentioned small gear in the another side, and possesses respectively the gas-cooled gas cooler that spues from above-mentioned the 1st stage compressor and above-mentioned the 2nd stage compressor, it is characterized in that, be equipped with lubricating oil tank in the bottom of said gear case; And on the bi-side by the above-mentioned lubricating oil tank below above-mentioned the 1st stage compressor and above-mentioned the 2nd stage compressor, be equipped with respectively the above-mentioned gas cooler; Each axis and the above-mentioned input shaft of above-mentioned lubricating oil tank and above-mentioned each gas cooler dispose abreast.
By such structure, can not increase the mechanical loss of turbocompressor and will be to the water supply and sewage pipe arrangement of gas cooler not crooked and be connected on each main pipe arrangement.Therefore, pipe arrangement construction is simpler, can also reduce to arrange the space, and these water supply and sewage pipe arrangements can not become obstruction aspect the safeguarding of above-mentioned compressor.
In above-mentioned relevant turbocompressor of the present invention, also can be, in above-mentioned lubricating oil tank, be provided with the isolating plate that the oily reservoir in the above-mentioned lubricating oil tank is divided up and down, form the aperture portion that the oily reservoir about the above-mentioned division is communicated with by the end of above-mentioned isolating plate and the inwall of above-mentioned lubricating oil tank.
By such structure, in the lubricating oil tank to accumulate the time elongated, can make the bubble collapse in the lubricant oil.As a result, can prevent decline and the corrosion of the lubricated and cooling capacity of said gear and bearing.In addition, can reduce the use amount of lubricant oil, the also small amount of capacity that makes lubricating oil tank, so the advantage that the size that produces compressor integral body also can miniaturization.
In above-mentioned relevant turbocompressor of the present invention, also can be that the above-mentioned gas cooler has heat exchanger, on the housing of above-mentioned gas cooler, is formed with the through hole of the above-mentioned heat exchanger insertion of confession at the axial direction of above-mentioned gas cooler.
By such structure, when the casting of this housing, core can be carried out two supports, can carry out reliably the sealing of gas cooler inside.
Description of drawings
Fig. 1 is the system diagram of signal of 3 grades of formula turbocompressor of relevant embodiments of the present invention.
Fig. 2 be relevant embodiments of the present invention 3 grades of formula turbocompressor omission the plan view of signal of motor.
Fig. 3 is that the A-A of Fig. 2 is to view.
Fig. 4 is that the B-B of Fig. 2 is to view.
Fig. 5 is the example that 3 grades of formula turbocompressor with relevant embodiments of the present invention arrange the system diagram of the cooling water pipe in many situation.
Fig. 6 is the plan view of the centrifugal compressor of relevant conventional art 1.
Fig. 7 is that IV-IV of Fig. 6 is to view.
Fig. 8 is the sectional view of the turbocompressor of relevant conventional art 2.
Fig. 9 is the example that the turbocompressor with relevant conventional art 2 arranges the system diagram of the cooling water pipe in many situation.
Embodiment
At first, for the turbocompressor of relevant embodiments of the present invention, as being applied to 3 grades of form examples in the formula turbocompressor, 1～Fig. 5 describes referring to accompanying drawing.Fig. 1 is the system diagram of signal of 3 grades of formula turbocompressor of relevant embodiments of the present invention, Fig. 2 be relevant embodiments of the present invention 3 grades of formula turbocompressor omission the plan view of signal of motor, Fig. 3 is that the A-A of Fig. 2 is to view, Fig. 4 be the B-B of Fig. 2 to view, Fig. 5 is the example that 3 grades of formula turbocompressor with relevant embodiments of the present invention arrange the system diagram of the cooling water pipe in many situation.
These 3 grades of formula turbocompressor possess the speed increaser (gear) 4 of the double-pinion type that 1-2 level small gear 7 and 8 engagements of 3 grades of small gears are formed as shown in Figure 1 in input gear 6.This speed increaser 4 is housed in the speed increaser housing (gear-box) 5.And above-mentioned input gear 6 in the central part place is connected on the input shaft 6a.In addition, input shaft 6a (not shown) such as bearings that be built in the speed increaser housing (gear-box) 5 is rotatably mounted.
Simultaneously, the end of above-mentioned input shaft 6a is outstanding from speed increaser housing 5, is connected on the output shaft 6b of motor M.Being connected via joiner 23 of above-mentioned input shaft 6a and output shaft 6b connects so that in the axle center also not vibration-generating and noise and transmit rotating force in the situation devious.Speed increaser housing 5 is made of the speed increaser lower shell body 5a of lower housing portion and the speed increaser upper shell 5b on housing top.And speed increaser lower shell body 5a is connected to the top of lubricating oil tank 13 described later.
In addition, on above-mentioned input gear 6, meshing 1-2 level small gear 7 and 3 grades of small gears 8, above-mentioned 1-2 level small gear 7 is subjected to pinion shaft 7a rotatably mounted, and then, above-mentioned 3 grades of small gears 8 are subjected to pinion shaft 8a rotatably mounted, namely, in other words, have pinion shaft 7a that the rotation of input shaft 6a is transmitted via input gear 6,1-2 level small gear 7 about 3 grades of formula turbocompressor of embodiments of the present invention and with the rotation of input shaft 6a via input gear 6,3 grades of pinion shaft 8a that small gear 8 transmits.
And, observe from speed increaser 4, connecting the 1st grade of impeller 1a at an end of the anti-motor M side of the pinion shaft 7a of 1-2 level small gear 7, be arranged with the 1st stage compressor housing 1b at the 1st grade of impeller 1a.On the other hand, observe from speed increaser 4, connecting the 2nd grade of impeller 2a at the other end of the motor M side of the pinion shaft 7a of 1-2 level small gear 7, be arranged with the 2nd stage compressor housing 2b at the 2nd grade of impeller 2a.In addition, this turbocompressor is observed from speed increaser 4, is connecting 3rd level impeller 3a at an end of the anti-motor M side of the pinion shaft 8a of 3 grades of small gears 8, and 3a is arranged with 3rd level compressor housing 3b at this 3rd level impeller.
These the 1st grade of impeller 1a, the 2nd grade of impeller 2a and 3rd level impeller 3a are accommodated in respectively in the vortex chamber (not shown) in the 1st stage compressor housing 1b, the 2nd stage compressor housing 2b and the 3rd level compressor housing 3b, consist of the 1st stage compressor 1, the 2nd stage compressor 2 and 3rd level compressor 3.
Namely, in these 3 grades of formula turbocompressor, possess the 1st stage compressor 1 that is driven by pinion shaft 7a in a side of speed increaser housing (gear-box) 5, and possess the 2nd stage compressor that is driven by pinion shaft 7a equally in another side of speed increaser housing (gear-box) 5.And, in these 3 grades of formula turbocompressor, on a side of speed increaser housing (gear-box) 5, possess the 3rd level compressor 3 that is driven by pinion shaft 8a, and possess the 3rd level compressor 3 that is driven by pinion shaft 8a in a side of speed increaser housing (gear-box) 5.
The air A0 that is inhaled into via not shown filter by suction is by 1 compression of the 1st stage compressor, is directed in the 1st grade of pressurized air stream 21 that the discharge opening with the 1st stage compressor 1 is communicated with the suction port of the 2nd stage compressor 2 as the 1st grade of pressurized air.And the 1st grade of pressurized air is directed in the 2nd stage compressor 2 through the 1st grade of interstage cooler (gas cooler) 11 that the 1st stage compressor that is folded in the 1st grade of pressurized air stream 21 of formation spues between pipe arrangement 21a and the 2nd stage compressor suction pipe arrangement 21b.
Import in the 2nd stage compressor 2 the 1st grade of pressurized air so that by 2 compressions of the 2nd stage compressor, be directed in the 2nd grade of pressurized air stream 22 that the discharge opening with the 2nd stage compressor 2 is communicated with the suction port of 3rd level compressor 3 as the 2nd grade of pressurized air.And the 2nd grade of pressurized air imports in the 3rd level compressor 3 through the 2nd grade of interstage cooler (gas cooler) 12 that the 2nd stage compressor that is folded in the 2nd grade of pressurized air stream 22 of formation spues between pipe arrangement 22a and the 3rd level compressor suction pipe arrangement 22b.And, constituting, the 3rd level pressurized air A3 that is compressed by this 3rd level compressor 3 is supplied with to compressed-air actuated demand motive ground.Here, reference character 20 is pipe joints that each pipe arrangement is connected.
And, the turbocompressor of relevant embodiments of the present invention is in 3 grades of formula turbocompressor as described above, 1-2 level small gear 7 and 3 grades of small gears 8 being engaged on the input gear 6 speed increaser 4 that forms below, and then be to be equipped with lubricating oil tank 13 in the bottom of speed increaser housing (gear-box) 5, on the other hand, below the 1st stage compressor 1, the 2nd stage compressor 2 and the 3rd level compressor 3 and on the bi-side of lubricating oil tank 13, be equipped with respectively the 1st grade of interstage cooler 11 and the 2nd grade of interstage cooler 12 with drum.
Simultaneously, when this turbocompressor is overlooked (with reference to Fig. 2), the input shaft 6a of lubricating oil tank axis C3 and the 1st grade of interstage cooler axis C1, the 2nd grade of interstage cooler axis C2 and compressor disposes abreast.Here, consisting of the 1st grade of interstage cooler body (housing) 11a of the shell of the 1st grade of interstage cooler 11, the 2nd grade of interstage cooler body (housing) 12a of shell that consists of the 2nd grade of interstage cooler 12 and the lubricating oil tank 13 that is clipped between these two interstage cooler body 11a, 12a forms by mo(u)lding.
In consisting of respectively above-mentioned the 1st grade and the 2nd grade of interstage cooler 11,12 the 1st grade and the 2nd grade of interstage cooler body 11a, 12a, preferably has the general cylindrical shape shape that is formed with through hole in each interstage cooler axis C1, C2 direction.And, in the through hole of the 1st grade and the 2nd grade interstage cooler body 11a, 12a, insert logical taken in heat exchanger 11b, 12b in each interstage cooler axis C1, C2 direction.
And then, constitute, supply with cooling water or discharge (with behind the pressure-air cooling) cooling water from these tube banks 11c, 12c to the tube bank 11c, the 12c that consist of heat exchanger 11b, 12b in these the 1st grade and the 2nd grade of interstage cooler 11,12, above-mentioned the 1st grade of pressurized air and the 2nd grade of pressurized air can be cooled off respectively.In addition, reference character 13a represents the lubricant oil case lid, and reference character 19a, 19b represent interstage cooler lid, in addition reference character 18, the 1st grade and the 2nd grade interstage cooler 11 of 18 expressions, 12 sealed department.
The water supply and sewage of cooling water is coordinated mouthful ( reference character 31,32 shown in Figure 5) according to reason described later, preferably certain side of the both end sides of each the interstage cooler axis C1 among the 1st grade and the 2nd grade of interstage cooler body 11a, the 12a, C2 direction is located at respectively on the 1st grade of anti-motor M side for example and the 2nd grade of interstage cooler lid 19a, the 19a.And, pull down, can carry out consisting of to inserting of the 1st grade and the 2nd grade of interstage cooler axis C1, C2 direction is logical of above-mentioned heat exchanger 11b, 12b by interstage cooler lid 19b, the 19b that the side that above-mentioned water supply and sewage coordinates mouthful will be installed.
Like this, by the 1st grade to 3rd level compressor 1,2,3 below and in the space of the bi-side of lubricating oil tank 13, be provided for gas-cooled the 1st grade and the 2nd grade of interstage cooler 11,12, can realize the compactness of compressor integral body.In addition, owing to made the logical structure of inserting to the 1st grade and the 2nd grade of interstage cooler axis C1, C2 direction that to carry out above-mentioned heat exchanger 11b, 12b, so heat exchanger I1b, 12b become simply to the 1st grade and the 2nd grade of interstage cooler 11,12 dismounting, each interstage cooler 11,12 maintenance become easy.And then, because the end face of the lubricant oil case lid 13a side of lubricating oil tank 13 do not hinder by motor, so become easy to the fuel feeding of lubricating oil tank 13 yet.
In addition, be formed with through hole owing to consist of the 1st grade and the 2nd grade of interstage cooler 11,12 the 1st grade and the 2nd grade of interstage cooler body 11a, 12a in these the 1st grade and the 2nd grade of interstage cooler axis C1, C2 direction, so when the casting of this interstage cooler body 11a, 12a, machining accuracy during the casting that core can be supported securely with its two ends and improve this interstage cooler body 11a, 12a can be carried out the 1st and the 2nd interstage cooler 11,12 sealed department 18,18 sealing reliably.
And then, the speed increaser housing 5 of taking in speed increaser 4 is made of the speed increaser lower shell body 5a of lower housing portion and the speed increaser upper shell 5b on housing top, lubricating oil tank 13 is formed on the bottom of speed increaser lower shell body 5a, and then, in the space of the bi-side of lubricating oil tank 13, be provided with the 1st grade and the 2nd grade of interstage cooler 11,12.By making such structure, can realize the compactness of relevant turbocompressor of the present invention, and by especially below lubricating oil tank 13 not but in the space of its bi-side the 1st grade and the 2nd grade of interstage cooler 11,12 are set, can make the gear 6～8 that consists of speed increaser 4 large with the distance change of the lubricated pasta of lubricating oil tank 13, so can eliminate the mechanical loss of bringing because of rebounding of lubricant oil.
Namely, in Fig. 4, the lubricant oil 14 that accumulates in the lubricating oil tank 13 is picked up by oil pump 17 from the not shown oil-feed port that is located on the lubricant oil case lid 13a, from the spray spout 10 of the spray spout 9 of 1-2 level small gear 7 usefulness and 3 grades of small gear 8 usefulness towards input gear 6,1-2 level small gear 7 and 3 grades of small gears 8 spray, be used for the lubricated of these speed increasers 4, cooling, even but rebounded from lubricated pasta 14b by the lubricant oil 14a that flies with the input gear 6 of the speed increaser 4 of High Rotation Speed and 3 grades of small gear 8 bullets, do not reach speed increaser 4 yet, can eliminate the mechanical loss of bringing because of rebounding of lubricant oil 14a.Here, reference character 24 is sense of rotation of input gear 6.
In addition, the turbocompressor of relevant embodiments of the present invention as shown in Figure 5, the interstage cooler of the anti-motor M side of the 1st grade and the 2nd grade of interstage cooler axis C1, C2 direction cover be respectively equipped with the 1st and the 2nd interstage cooler 11,12 water supply coordinate mouthfuls 31,31 and draining coordinate mouthfuls 32,32, so above-mentioned turbocompressor arranged in many situation, coordinate to supplying water mouthfuls 31 and draining coordinate mouthful 32 water supply piping 31a that connect and drainage piping 32a can both be not crooked and connect with respect to supply water main pipe arrangement 31b and draining master pipe arrangement 32b.
Namely, water supply piping 31a and drainage piping 32a are after generally perpendicularly extending from supply water main pipe arrangement 31b and draining master pipe arrangement 32b, not crooked, and to be configured in this water supply piping 31a and drainage piping 32a roughly coaxial water supply coordinate mouthfuls 31 and draining coordinate mouthfuls 32 and be connected.Therefore, the pipe arrangement construction is simpler, can also reduce to arrange the space, and these pipe arrangements can not become the obstacle of the maintenance of compressor.
And then turbocompressor such as Fig. 2, shown in Figure 4 of relevant embodiments of the present invention in lubricating oil tank 13, are provided with the isolating plate 16 that the oily reservoir 15 in this case 13 is divided up and down.In addition, form the aperture portion 16a that will be communicated with by the oily reservoir up and down 15 that isolating plate 16 is divided by the end of this isolating plate 16 and the inwall of case 13.
The lubricant oil 14 that is flown by speed increaser 4 bullets and accumulate in the oily reservoir 15 is picked up by oil pump 17 from the not shown oil-feed port that is located on the lubricant oil case lid 13a, again for input gear 6,1-2 level small gear 7 and 3 grades of small gears 8, also have lubricated, the cooling of not shown bearing, but by the lubricant oil 14a that said gear 6～8 bullets with High Rotation Speed fly air (bubble) is involved in and gets back in the oily reservoir 15 in the lubricating oil tank 13.The lubricant oil 14 that contains the state of this bubble becomes the decline of the ability of said gear 6～8 and bearing lubrication, cooling and the reason of corrosion.
As the method that bubble is eliminated, generally be the volume that increases lubricating oil tank 13, make the time of returning till the lubricant oil 16 that comes is reused elongated, bubble floating is played on the pasta and the method for dispersing, but need so a large amount of lubricant oil 14.By isolating plate 16 is set as described above, till being inhaled in the oil pump 17 to lubricant oil 14, flown by said gear 6～8 bullets and drop to lubricant oil 14 on the lubricated pasta 14b of oily reservoir 15 along the flowing of lubricant oil 14 of the oily reservoir 15 that is isolated the upside that plate 16 divides and via aperture portion 16a, then along the flowing of lubricant oil 14 of the oily reservoir 15 that is isolated the downside that plate 16 divides and towards lubricant oil case lid 13a direction.
Therefore, advance along long path reliably till being inhaled in the oil pump 17 to lubricant oil 14, the time till recycling is elongated, and the bubble floating in the lubricant oil 14 plays on the pasta, so bubble is dispersed to the gas phase sections in the speed increaser housing 5.
In the situation that does not have isolating plate 16, drop to from speed increaser 4 lubricant oil 14 on the lubricated pasta 14b of lubricating oil tank 13 with shortest path towards lubricant oil case lid 13a, and compare with it, in the situation of the embodiments of the present invention that are provided with isolating plate 16, the above-mentioned lubricant oil 14 that drops on the lubricated pasta 14b of lubricating oil tank 13 is gone out in the lubricating oil tank 13 via the distance of about 3 double-lengths.
As described above, according to the turbocompressor of relevant embodiments of the present invention, can make as the bubble collapse in the lubricant oil 14 that lubricates the decrease reason that reaches cooling capacity of speed increaser 4 and bearing.And then, can reduce the use amount of lubricant oil 14, the volume that can make lubricating oil tank 13 is small amount also, so produce the also advantage of miniaturization of size that can make compressor integral body.
In addition, turbocompressor about relevant embodiments of the present invention, illustrated and be applied to 3 grades of form examples in the formula turbocompressor, but relevant turbocompressor of the present invention is not limited to 3 grades of formula turbocompressor, also is effective certainly in 2 grades of formula turbocompressor or the multistage turbocompressor more than 4 grades.
Claims (3)
1. a turbocompressor having on input shaft and the acceptance side via the gear-box of at least 1 pinion shaft of the rotation of the next above-mentioned input shaft of gear transmission, possesses by shaft-driven the 1st stage compressor of above-mentioned small gear,
And possess by shaft-driven the 2nd stage compressor of above-mentioned small gear in the another side,
And possess respectively the gas-cooled gas cooler that spues from above-mentioned the 1st stage compressor and above-mentioned the 2nd stage compressor, it is characterized in that,
Bottom at the said gear case is equipped with lubricating oil tank;
And on the bi-side by the above-mentioned lubricating oil tank below above-mentioned the 1st stage compressor and above-mentioned the 2nd stage compressor, be equipped with respectively the above-mentioned gas cooler;
Each axis and the above-mentioned input shaft of above-mentioned lubricating oil tank and above-mentioned each gas cooler dispose abreast.
2. turbocompressor as claimed in claim 1, it is characterized in that, in above-mentioned lubricating oil tank, be provided with the isolating plate that the oily reservoir in the above-mentioned lubricating oil tank is divided up and down, form the aperture portion that the oily reservoir about the above-mentioned division is communicated with by the end of above-mentioned isolating plate and the inwall of above-mentioned lubricating oil tank.
3. turbocompressor as claimed in claim 1 or 2 is characterized in that, the above-mentioned gas cooler has heat exchanger, on the housing of above-mentioned gas cooler, is formed with the through hole of the above-mentioned heat exchanger insertion of confession at the axial direction of above-mentioned gas cooler.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011199770A JP5616866B2 (en) | 2011-09-13 | 2011-09-13 | Turbo compressor |
| JP2011-199770 | 2011-09-13 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102996471A true CN102996471A (en) | 2013-03-27 |
| CN102996471B CN102996471B (en) | 2015-12-02 |
Family
ID=47925453
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210335844.2A Expired - Fee Related CN102996471B (en) | 2011-09-13 | 2012-09-12 | Turbocompressor |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP5616866B2 (en) |
| KR (1) | KR20130029022A (en) |
| CN (1) | CN102996471B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108895154A (en) * | 2018-08-15 | 2018-11-27 | 吉林省京能水处理技术有限公司 | A kind of gear-box for wind power generation function |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN203297122U (en) * | 2013-04-26 | 2013-11-20 | 株式会社神户制钢所 | Compression unit |
| JP6395683B2 (en) | 2015-09-02 | 2018-09-26 | 株式会社神戸製鋼所 | Compressor |
| KR102558545B1 (en) * | 2016-06-02 | 2023-07-21 | 한화파워시스템 주식회사 | Compressor and compressor system |
| JP6617992B2 (en) * | 2016-06-10 | 2019-12-11 | 三菱重工コンプレッサ株式会社 | Compressor module |
| DE102016113067A1 (en) * | 2016-07-15 | 2018-01-18 | Man Diesel & Turbo Se | Geared turbine machine |
| WO2018150541A1 (en) | 2017-02-17 | 2018-08-23 | 三菱重工コンプレッサ株式会社 | Compressor module |
| US20220268526A1 (en) | 2021-02-25 | 2022-08-25 | Mitsubishi Heavy Industries Compressor Corporation | Compressor module and compressor module designing method |
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| US20030059299A1 (en) * | 2001-09-25 | 2003-03-27 | Haruo Miura | Turbo compressor |
| JP2003328998A (en) * | 2002-05-17 | 2003-11-19 | Kobe Steel Ltd | Turbo compressor |
| JP2007332826A (en) * | 2006-06-13 | 2007-12-27 | Kobe Steel Ltd | Centrifugal compressor |
| JP2008133746A (en) * | 2006-11-27 | 2008-06-12 | Ihi Corp | Turbo compressor |
| CN101504004A (en) * | 2008-02-06 | 2009-08-12 | 株式会社Ihi | Turbo compressor and refrigerator |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3480009B2 (en) * | 1993-10-04 | 2003-12-15 | 石川島播磨重工業株式会社 | Centrifugal compressor |
-
2011
- 2011-09-13 JP JP2011199770A patent/JP5616866B2/en not_active Expired - Fee Related
-
2012
- 2012-09-12 KR KR1020120100993A patent/KR20130029022A/en not_active Application Discontinuation
- 2012-09-12 CN CN201210335844.2A patent/CN102996471B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030059299A1 (en) * | 2001-09-25 | 2003-03-27 | Haruo Miura | Turbo compressor |
| JP2003328998A (en) * | 2002-05-17 | 2003-11-19 | Kobe Steel Ltd | Turbo compressor |
| JP2007332826A (en) * | 2006-06-13 | 2007-12-27 | Kobe Steel Ltd | Centrifugal compressor |
| JP2008133746A (en) * | 2006-11-27 | 2008-06-12 | Ihi Corp | Turbo compressor |
| CN101504004A (en) * | 2008-02-06 | 2009-08-12 | 株式会社Ihi | Turbo compressor and refrigerator |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108895154A (en) * | 2018-08-15 | 2018-11-27 | 吉林省京能水处理技术有限公司 | A kind of gear-box for wind power generation function |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5616866B2 (en) | 2014-10-29 |
| KR20130029022A (en) | 2013-03-21 |
| CN102996471B (en) | 2015-12-02 |
| JP2013060882A (en) | 2013-04-04 |
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